Wind rotor



Oct. 11, 1949. l R. R, HAYS 2,484,291

WIND KOTOR Filed July 15, 1945 4 Sheets-Sheet l VENToR, l ZDz/ffd/ /P /Vg/s.

Oct. 11, 1949. R. R. HAYs 2,484,291

l I WIND ROTOR Filed July 15, 1945 4 sheets-sheet IN1/EN TOR, 27mm ys.

Oct. 1l, 1949. R. R. HAYS 2,484,291

WIND RoToR Filed July 13, 1945 4 sheets-sheet s Oct. 1l, 1949. R, R, HAYS 2,484,291

WIND KOTOR Filed July 13, 1945 l 4 Sheets-Sheet 4 y IN1/'Lw roR,

Patented Oct. 11, 1949 UNITED STATES PATENT OFFICE 6 Claims.

This invention relates to wind rotors used for 'obtaining power from the Wind, and more particularly to the mounting of such a rotor on a tower and for the direct operation of an air cornpressor mounted as a unit with the rotor hub.

While the term rotor is used loosely to describe any rotating airfoil system, it has come to have a more speciiic meaning in the eld of aeronautics in that it defines a lifting propeller or horizontally disposed airfoil system in which the blades are mounted for free rocking action about an axis transverse to their axis of rotation in response to airilow dissymmetry arising when operating in yaw. This rocking or flapping acts to equalize thev lift on the blades at opposite phases of rotation, and thus permits operation of a rotor at large angles of yaw without producing an excessive overturning couple.

In this invention it is proposed to use such a rotor, not alone because initial tilting of it with respect to the vertical permits the use of a smaller and lighter supporting tower such as described in co-pending application Serial No. 559,454 (Patent No. 2,454,058, dated November 16, 1948), but also to damp out unbalanced forces arising through sudden changes in the direction and velocity of the wind. This latter permits greatly reduced structural strength in both the rotor and the supporting tower. In attaining this end it is further desirable that the rotor function as a vane for maintaining it in the wind and also for turning it partially out of the wind when the latters velocity becomes excessive.

The latter end is achieved not alone by mounting the rotor downwind with respect to the supporting tower, but also by twisting its plane of rotation with respect to a vertical plane containing its center of thrust and the pivot axis of the head on which it is mounted. Twisting a tilted rotor in this manner and offsetting it from the head pivot are necessary for balancing the torque couple resultant to the initial tilting from the vertical which acts to throw the rotor out of the wind. The mechanical principle involved is broadly similar to that used in a conventional single rotor helicopter for balancing the torque couple by tilting the rotor to obtain a lateral component of the thrust.

If for the moment we assume that a win-d rotor has been initially tilted, twisted, and offset with respect to the tower head on which it is mounted so that it tends, when supplying a useful torque, to maintain its plane of rotation substantially transverse to the direction of the wind, we may then consider broadly some of the problems arising in response to sudden fluctuations in both velocity and direction of the wind. Basically a rotor is a gyroscopic mass, and unless provision is made for damping of movement about three transverse axes, forces arising on it in response to sudden movement tend to be passed on in their entirety to the supporting structure. This a-lone would be reason for incorporating an axis transverse to the pivot shait of the supporting head to permit limited vertical movement of the rotor assembly. In this instance, however, such a transverse head shaft is also utilized to automatically synchronize the compressor load with the power available.

The reason such synchronization is necessary is because the power generated by a wind rotor varies as the cube of the wind velocity, whereas the forces effective on the rotor itself vary only as the square of the wind velocity. In short, the eect of an increase in wind velocity upon the rotor is two-fold; the thrust on the blades increases as the velocity squared, and this in turn acts to increase the rotational velocity of the rotor by an equivalent degree. Since the power absorbed by a conventional air compressor varies roughly as its R. P. M. it follows that power generated in excess oi the wind velocity squared is largely dissipated by increasing the rotational speed of the rotor to produce inelicient and even negative attack angles at the blade tips.

The obvious solution to this problem is one of increasing the capacity of the compressor coincident with an increase in the velocity of the wind. rIhis end is achieved by using a multiple cylinder compressor and successively closing bleeder valves from these cylinders as the available power increases. Such an arrangement further permits instantaneous loading and unloading of the rotor which has been found to be highly desirable both in starting it and when a gust of wind suddenly dies away. Synchronization of the bleeder valves with the power deflivered by the rotor might be achieved by the use of an ordinary centrifugal governor were it not for this need to quickly unload and load the rotor irrespective of its rotational speed. This latter condition arises, for instance, when the wind suddenly dies. Because of its rotational speed and the mass of the blades the inertia of the rotor continues to supply a large torque to the compressor, and hence this torque is effective at the rotor hub to turn it out of the wind. The lift force opposed to this torque couple has meantime ceased due to stoppage of the wind with the result that the rotor pivots about the main pivot F shaft unless throwout be used to stop the torque to the compressor at the same time.

By lio-.'izontally hinging the inner end of the offsetting arm on which the rotor unit is mounted, variations in -lift of the rotor may ce utilized directly for raising and lowering the arm, nd. is in turn 1used to throw the bleeder valves f the compressor. However, since raising of arm acts directly to increase the initial tilt of rotor to the Vertical, and hence the value of torque couple available for turning the rotor of the wind, it follows that it is necessary siwuitaneously twist the rotor by an amount ifiicient to increase the horizontal lift comonent opposed to this couple by an equivalent Oree. This end is achieved by canting the ntal hinge axis relative to the rotor disc liat the desired increase in the horizontally `g component is automatically obtained with g oi the oisetting arm.

th these general considerations inz mind the tlsese ends may be more clearly del Accordingly, the objectives of this inven- .rlon may be defined as:

1. The provision of a wind rotor operating in yaw and mounted on an offsetting arm from the units main pivoting axis and with the rotors axis of rotation canted with respect to this offsetting arm by such a degree that a torque couple tending to swing the rotor out of the wind is balanced by a horizontal component of the lift on the rotor acting through a moment arm defined by the offsetting arm on which the rotor unit is mounted.

2. The provision of an offsetting arm carrying a wind rotor compressor unit which is aXed by a hinge to the main pivot head to permit relative raising and lowering of the arm and the unit carried by it.

3. Provision of a wind rotor-compressor unit in which a planetary gear unit intermediate the rotor drive shaft and a multiple cylinder compressor steps up the R. P. M. of the rotor drive shaft in driving the compressor to permit the use of a smaller compressor and to more evenly distribute the compressor load during the single revolution of the rotor.

4. Provision of a hinged off-setting arm with such a rotor-compressor unit mounted on its eX- tending end and having stops at its inner end to limit downward movement of the arm with the result that the weight of the unit acts to damp upward movement of the extending end of the arm in response to lift, torque, and gyroscopic forces tending to raise it during operation.

5. Provision of hinged eff-setting arm for carrying a rotor-compressor unit the hinge of which is normally in a horizontal plane and canted with respect to the rotor disc so that raising of the unit tends to twist the rotor with respect to the head pivot as well as farther tilt the rotor Iwith respect to the Vertical.

6. Frcvision of a compression spring for damping downward movement of a rotor-compressor unit mounted on an onf-setting arm, and urging it through a limited degree of upward movement, and a pushrod operated by the compression spring which acts to successively close bleeder valves of the compressor cylinders with upward travel of the offsetting arm and to close them in the same order during downward travel.

'7. Provision of a wind rotor-compressor mounted en an offsetting arm and canted laterally thereto to provide a horizontal component of the rotor lift effective as a vane opposed to 4 torque forces tending to turn the rotor out of the wind, and becoming increasingly effective when the power available from the wind exceeds the compressor capacity so that it acts to pull the rotor out of the wind in the direction of this horizontal lift component.

8. Provision of a hinged offsetting arm carrying a rotor-compressor unit movement of which is automatically responsive to wind velocity variations and automatically maintains the bleeder valves of the compressor open until the rotor initially builds up speed in starting; and when in operation automatically opens these bleeder valves when the thrust or lift on the rotor decreases to that of the initial bleeder valve closing position.

Ancillary objectives such as the provision of a compact rotor-compressor unit, bleeder valves and a push rod for opening them, check valves for each cylinder, means for carrying the compressed air through the main pivot shaft and the like, will be claried by the following description taken in conjunction with the accompanying drawings in which:

Figure 1 is a perspective View in elevation illus3 trating in dotted lines variation in the tilt and twist angles of a wind rotor such as that embodied in this invention.

Fig. 2 is an enlarged view in side elevation of the crown pivot and the transverse bearing on ,i which the rotor compressor unit is mounted.

Fig. 3 is a View in side elevation of the rotor bearing-compressor unit.

Fig. 4 is a view taken from above of the unit shown in Fig. 3.

Fig. 5 is an enlarged sectional View of the rotor bearing and planetary gearing which drives the compressor shown in Fig. 4 taken along line 5 5 of this figure.

Fig. 6 is a cross sectional view of the planetary gearing of the rotor-compressor unit taken along the line S-S of Fig. 5.

Fig. 7 is a cross-'sectional View of the bleeder valve throw spring taken along the line l-'l of Fig. 4.

Fig. 8 is an irregular diagrammatic sectional plan View of the leads to the bleeder valves and the check valves through which they open into the main air line.

Fig. 9 is an irregular, so-mewhat diagrammatic vertical section taken along the line 9--9 of Fig. 6.

Fig. l0 is a diagrammatic sketch taken in perspective of the wind rotor shown in Fig. l in which the torque couples arising in response to tilting and twisting of the rotor are shown.

Fig. 11 is a diagrammatic sketch taken from above the rotor in Fig. 10 in which are shown the forces required to prevent rotation of a tilted rotor about the crown pivot.

Fig. 12 is a diagrammatic sketch in side elevation of a rotor-compressor unit illustrating the damping action of the unit to forces arising through tilt and twist of the rotor relative to the crown p1vot.

Fig. 13 is a diagrammatic plan form sketch of the rotor-compressor unit taken from above Fig. 12 in which is shown the effect of Canting the transverse crown pivot to maintain balance between the forces effective upon the unit with movement about the transverse pivot.

Referring to the drawings, the legs l5 of a conventional steel tower I4, Fig. 1, converge into a crown bearing I6 which carries the pivotally mounted crown or head i8 to which is hinged the arms rigidly secured at their outer ends to the bearing case 2| of the rotor bearing-compressor unit 22 the outer end of which comprises a hub 26 on which is mounted a conventional rotor 25 having interconnected blades 21 and 28 such as those shown and described in Patent No. 2,369,048. In this type of Windmill, usually referred to as a highspeed wheel and having a tipspeed ratio of 3. or better to distinguish it from the slower, higher solidity wheels having tipspeed ratios of 2. or less, the pitch of the blades is quite small and consequently an aircraft rotor suitable for auto-rotative descent is easily converted to such a windmill by slightly varying the pitch of the blades.

The torque produced by the rotor is trans-4 mitted through the pivotal mounting 29 to the hub 26, Figs. 3, 4, and 5, solidly affixed to the rotor shaft 38 carried by combination bearings 32 and 33 of the bearing case 2l having a grease chamber 35 intermediate the bearings 32 and 33 and filled through the alemite fitting 36. The inner end of the shaft 38 carries a bell gear 38 the internal teeth 39 of which are contacted by planet gears 40, Fig. 6, mounted on stub shafts 42 carried in the compressor crank case 50 which drive the sun gear 44 fixed to the extending end of the compressor crankshaft 46 carried by the compressor main bearing 41 aligned with rotor bearings 32 and 33. The forward face 48 of the compressor crankcase 5U is fixed to the bearing case 2| by suitable bolts 49 and serves to maintain alignment of shafts 46 and 30 to make a single compact unit of the compressor 24, bearing case 2| and gears 38, 48 and 44.

The purpose of the gears is two-fold. In the first place they step up the R. P. M. of the rotor shaft 38 and thus permit the use of a considerably lighter compressor than would otherwise be required to absorb the available torque. The second factor is that the load on a compressor is greatest during the compression stroke and this gives rise to periodic movement of an anticulal tively mounted rotor-compressor unit which becomes quite noticeable when the compressor is turned directly by the rotor. By increasing the number of compressor impulses per rotor R.. P. M. the magnitude of these impulses is decreased by a like degree and a marked increase in the smoothness of operation results.

The compressor 24 has multiple cylinders 52,l 53, 54 and 55 with exhaust lines 56, 57, 58 and 59 respectively connecting them directly to bleeder valves 62, 63, 84 and 65 respectively carried in the valve throw box 60. Air inlet Valves 5I of each cylinder are normally connected with an air il ter, not shown, by lines similar to 56-59. The purpose in having multiple cylinders on the compressor 24 is that of extending the range over which the compressor can completely absorb the power generated by the rotor 25. Since the power available increases as the cube of the wind velocity, whereas the power absorbed by a single cylinder 52 increases only as the square of the wind Velocity, it follows that where air is delivered at a constant pressure the capacity of the compressor should also be variable directly as the wind velocity. Hence, if the rotor be designed to carry one cylinder in a wind of 8 M. P. H., two cylinders will be required to carry the load at 16 M. P. H. and all four cylinders will be needed when the wind velocity reaches 32 M. P. H. at which time the volume of air delivered will be in the neighborhood of 32 times that delivered at 8 M. P. H., less an amount. arising as a result of des creased compressor efficiency resultant to more rapid operation.

Variation in the capacity of the compressor 24 is synchronized with variations in wind velocity by reason of variation in the lifting force L acting on the rotor. The force L will vary substantially as the wind velocity squared and when its line of action which is more or less coincident with the axis C-C of of the rotor shaft 3l] lies below the transverse crown axis B-B, it will exert a force Lv, Fig. 12, tending to rotate the entire rotor-compressor unit upward and about the axis of B-B. This force Lv is opposed by the weight G of the unit which is normally of considerably greater magnitude. However, by counterbalancing the weight G of the unit by a variable tension compression spring 12 carried in a cylindrical case 14 integral with the Valve throw box 60 which forms its outer end and is solidly afxed to the bottom of the compressor crankcase 58, the entire rotor-compressor unit can be caused to swing away from the head I8 in response to rotor lift variations by a predetermined degree, which incidently produces a slight increase in the tilt angle of the rotor as illustrated in Fig. 1.

Considering the valve throw mechanism more in detail Fig. 7, a pushrod 16 carries on its inner end a piston 18 which contacts the inside wall of the spring case 14 and projects therefrom as a push arm 19 which normally contacts the step |26 of the head I8. The pushrod 18 passes through the compression spring 12 and through the opposite end 88 of the spring case 14, being threaded on its extending end 82 into the push plate 84, Fig. 9, where its length and hence the initial tension of the compression spring 12 may be adjusted after which it is locked in position by setscrew 85. It is thus apparent that the compression spring 12 is effective in pushing the rotor-compressor unit away from the head I8 and about the axis B--B through the distance D, Fig. rI, after which movement of the pushrod 16 and hence the spring 12 will be restrained by the push plate 84 contacting the outer face of the cylinder end 80. Hence the tension of the spring 12 can be predetermined and the adjustment made of the respective parts such that with a wind velocity of, for instance, 8 M. P, H., the lift L of the rotor will be sufficient to swing the rotorcompressor unit away from the head I8 through an arc of D/4, at 16 M. P. H. through an arc of D/2, and so progressively on out until the push plate 84 contacts the end of the spring case, after which the tension of the spring 12 will no longer be effective in counterbalancing the weight G of the unit.

This motion of the push plate 84 is utilized directly for opening the staggered bleeder valves 62, 63, 64 and 65 carried in the upper wall section of the valve box 60. The purpose of the bleeder valves is to prevent compression of air in the cylinders of the compressor until there is rotor torque suflicient to handle it. In short, all the bleeder valves are open when the wind rotor 25 is idle and the spring 'I2 is taking its maximum compression load. Taking the bleeder valves individually, the airline 58 leading from compressor cylinder 54 is connected with the passage 92 in the valve box 60 by means of a conventional tubing connection 9|, Fig. 9. The vertical well 94 drilled in section 90 and connecting with passage 92 ends in valve seat 95 ush with the face 89 of yvalve boxwall section 90 on which pushplate S4 rides, and the ball 96 seating in valve seat 95 normally projects past the plate face 89 so that rearward movement of pushplate 84 acts to raise it ofi` its seat 05, thus permitting air to escape from compressor cylinder 64. With forward movement of pushplate 84, the coiled spring 9'! carried in the well 04 by hollow plug 98 seats the ball 96 in the bleeder valve seat 95. With closing oi valve $5 air from cylinder 64 continues down the passage S2 and through the well 94 to the check valve well |00 the bottom of which also comprises a valve seat IOI seating ball |02 which is normally held in a seated position by compression spring EUR carried by the hollow plug i. ence when air from cylinder 64 raises ball valve i232 it is led from well |00 through passage it? into the main air gathering passage |09 having outside i'ltting I|I connecting it with the exible air line I I2.

In this instance the bleeder valves G2, 63, 64 and G5 are located diagonally in the upper section 90 of the valve throw box 50, Fig. 8, with respect to the transverse bull-nose lip 81 at the rear face of the push plate 34, the width of the latter being such that all valves are held open when the push plate attains the maximum travel rearwardly, and successively close with forward travel of plate 84 through the action of springs 0T until all are clear of push plate 85| when it reaches the limit of its forward travel. Air under compression passing through flexible tube H2 is conducted into the passageway IIE by fitting IIl at the inner end of tube II2 and is led down through the center of the vertical pivot shaft IIS mounted in suitable bearings in :ff:

the crown i8 of tower I4, a smaller extension |20 of shaft M8 being seated in a conventional packing gland and 'rotatable chamber combination |22 tted to conduit tube |24 by which it is conducted down a leg of tower I4 to a storage reservoir such as that described in co-pending application Serial No. 559,454.

The body |30 ol pivotally mounted head I8 on which the .rotor compressor unit 22 is mounted by arms carrying transverse shaft I9 mounted in transverse head bearing at its top is formed out of alignment with its pivotal axis A-A to provide clearance for the unit 22 and its base |21 cut in a step |26 which contacts the extending end 'EQ o1" pushrod 7S. When the unit 22 is raised through large angles with respect to the head i8, a stop |32 on one of the unit arms 20 contacts the body |30 of the head to prevent extreme upward travel o the unit induced by sudden changes in wind velocity above the rotors normal range of operation.

The precise position of the rotor-compressor unit 22 with respect to the pivotal head i8 to provide balance between torque and lift forces effective upon the unit during operation, are dependent upon the lift torque curve of the particular rotor used, but the angular relationships required to obtain such balance in the rotor are basically the same for all units of this type. Referring to Fig. 10, the rotor 25 is seen during operation to have two characteristic forces created upon it in 'response to the force of the wind W. The greater of these is a lift force L acting mole or less in alignment with the rotors axis oi rotation C-C, and a lesser torque force in the rotors plane of rotation acting to turn it and to supply a useful torque T which may be considered as acting through the blades center of percussion c. p. and having a moment arm N 8 which is the distance of the c. p. from the rotor axis C-C.

With tilting of the rotor 25 from the vertical and hence through an angle X to the pivotal axis A-A, the torque T absorbed by the compressor 24 developes a horizontally acting component T equal to the sine XT, which referred to the pivotal axis A-A, Fig. 11, becomes the force Th having a moment arm M which is the distance of the rotor 25 from the pivotal axis A-A. To prevent the rotor being pulled out of the wind by the force Th the rotor 25 is twisted laterally with respect to the offsetting arm Z0 through an angle O, so that the rotor lift L has a moment arm Q relative to the pivotal axis A-A. The hori zontally acting lift component Ln resultant to such twisting of the rotor is seen to equal Tn when:

and the rotor tends to maintain itself transverse to the wind despite the fact that it is tilted from 'the vertical.

When we take rotor initiaily balanced in this fashion and mount it for movement about a orizontal axis 'i3- 13, which in this instance intercts axis A-A, Fig. l2, several things happen. For one thing, lateral twisting of the rotor with respect to the osctting arnis 2li produces a vertical component T of the torque T which referred to the axis B-B becomes a vertical force Tv having the moment arm M. This acts to raise the 22 about the axis B-B and is resisted by the units weight G acting through its center of gravity e. g. Since he force Tv varies directly as the torque utilized by the compressor 24 it is not desirabie to use it for throwing the compressor bleeder valves. Instead, a vertical component L; of the lift L is made available by raising the axis B-B with respect to the lift axis C-C, thus giving the liit L a moment arm J with respect to the axis B-B which referred to the center of the rotor becomes a vertical component Lv of the lift L having a moment arm M which tends to -e the unit 22, and is restrained by the latters weight G as is the vertically acting torque component Tv.

'in general the weight G of the unit 22 should be slightly greater than Tv and Lv combined when all four cylinders of the compressor 24 are in operation, and Tv should be less than G minus rnaxiimnn tension of compression spring 12,

tri-.6 when the rotor is carrying its peak load since otherwise with a sudden drop in wind velocity the compressor' bleeder valves would not be thrown to give the equivalent of free wheeling of the rotor.

With raising of rotor-compressor unit 22 by increase in the vertically acting components of lift and torque effective upon the rotor, the direct effect is one of increasing the tilt angle of rotor with a subsequent increase in the horizontal torque component Th, but when the hinging axis B-B is parallel to the plane of the rotor disc there is no associated increase in the horizontal lift component Lil. In order that Ln may increase by an equivalent degree to maintain balance oi the system, the axis B-B of the oiisetting arm 20 canted in a horizontal plane oppositely to the direction of rotor twist through an angle Z, which for the condition." set up in this instance is an angle of about 45. As a result of this canting, raising of the unit 22 produces an increase in the twist angle O of the rotor thereby increasing Ln by an amount (e) substantially equal to the simultaneous increase of Th by the amount (t), Fig. 13.

While a great deal of variation in the value of the angularity required to obtain balancing of the rotor forces is to be expected, inasmuch as the lift/torque ratio varies widely with different rotors, the principle involved remains the same. For example, with rotors having a high lifttorque ratio the value of the twist angle O will be decreased. Or if it is desirable to lengthen the offsetting arms 20, the twist angle O and the included angle Y may :be decreased, and the hinge angle Z increased. Normally an increase of of the tilt angle X of the rotor through raising of the unit 22 should be adequate for closing all the bleeder valves, but greater or less travel may be used, dependent upon the weightof the rotor-compressor unit which may be plotted as a lift/weight ratio in computing the angularity desired.

In operation, too short an oii'setting arm 2Q makes the rotor sluggish in following the wind. This is not desirable, since a well balanced rotor will operate for a considerable period in an upwind position and rotating backwards before swinging around into a downwind position and reversing its direction. With suitable length to the offsetting arm 20, the rotor swings slowly into a downwind position before beginning to turn. Since the power produced in wind velocities under 8 M. P. I-I. is insignificant, and since the efficiency of the rotor is of a low order until after it obtains its rated tipspeed ratio it is desirable that no load be imposed upon it at speeds less than 8 M. P. H. Hence, the bleeder valves are maintained open until the lift L at this wind velocity raises the unit 22 and the push-plate 84 moves forward to let one of the bleeder valves close. This preliminary revving up is particularly desirable since the compressor usually has to buck pressure in the air line |24. What actually occurs is that due to its twist, the lift on the rotor acts to pull it into a position slightly transverse to the wind while free-wheeling, and with lclosing of the bleeder valve the torque then pulls it directly into the wind. Imposition of the torque load acts to slow the rotor slightly and decrease Lv but the torque Tv comes into being at the same time and acts to maintain the unit 22 in its initially raised position. And it is obvious that the relative values of Tv to Lv required to obtain smooth transition from free-wheeling may be varied by variation in the value of the distance J through raising or lowering of the unit 22 with respect to the hinge axis B-B. This same operation is repeated in the closing of the remaining bleeder valves.

It will be observed that the compression throw spring 'l2 is initially placed under tension by the pushrod 16. The purpose of this is that after all the bleeder valves have been opened, the damping value of the weight `of unit 22 is abruptly increased by the amount of this initial tension. Thus, the tilting increase of the rotor is normally limited to the throw of the spring 12, but freedom of the unit 22 to raise in response to overloads is still possible. These are of two types. One occurs with sudden shifts in the wind when the unit 22 raises slightly, evidently in response to some gyroscopie force the exact nature of which is not known. The other overloads occur when the wind velocity becomes excessive, which in this case is at air speeds above 32 M. P.I Above rapidly than the torque utilized by the compressory with the result that unit 22 is raised and at the same time the lift component Lh acts to pull the rotor slightly out of the wind.

With gradual dying of the wind theinertia of the rotor provides a lag to the torque so thatv the latter pulls the rotor slightly out of the wind. When the wind suddenly dies, however, as is often the case, the unit 22 drops down, compressing the spring 'l2 and opening the bleederV valves from the compressor so that the rotor free-wheels. does not take place, the rotorss inertia acting through the torque swings the rotor unit around into an upwind position, or may even cause it vto make a complete revolution about the axis A-A, but in either case causes no undue stresses or breakage of parts.

As many changes could be made in carrying out the above construction without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

Having thus described my invention, what I claim as new and desire to be secured by Letters Patent is: l

l. In a wind rotor-compressor unit for ,converting wind energy to a contained constant pressure airstream, a tower, a pivotal mounting for said unit on said tower providing freedom for the rotor of said unit to assume a downwind position with respect to said tower, a second pivotal mounting intermediate said tower and said unit canting said unit with respect to said rst pivotal mounting and permitting limited move-l ment of said unit in response to a vertical com- 2. In a wind rotor-compressor unit for converting wind energy to a contained constant pressure airstream, a tower, a pivotal mounting for said unit on said tower providing freedom for the rotor of said unit to assume a downwind position with respect to said tower, a second pivotal mounting intermediate said tower and said unit canting said unit with respect to said first pivotal mounting and permitting limited movement of said unit in response to a vertical component of the lift effective upon said rotor and means operatively associated with said second pivotal mounting, including a multiple cylinder air compressor and bleeder valves succes- .sively opened and closed in response to said limited movement of said unit whereby the capacity of said compressor is automatically varied in response to lift variations on said rotor.

3. In a wind rotor-compressor unit for converting wind energy to a contained constant pressure airstream, a tower, a pivotal mounting for said unit on said tower providing freedom for the rotor of said unit to assume a downwind position with respect to said tower, a second pivotal mounting intermediate said tower and said unit canting said unit with respect to said first pivotal mounting and permitting limiting movement of said unit in response to a vertical component of the lift eifective upon said rotor and means operatively associated with said second pivotal mounting, including a multiple cylinder air .compressor and bleeder valves successively If for any reason free-wheelingy opened and closed in response to said limited movement of said unit, and variable tension means directly responsive to the liit of said rotor for maintaining said bleeder valves open at rotor lift values below the rotors normal opererating range whereby said rotor free-wheels to get up its rated tipspeed ratio before having a torque load imposed upon it, and also free-wheels to remove said torque load when said rated tipspeed ratio is exceeded due to a sudden decrease in the velocity of the wind.

4. In a wind rotor-compressor unit for converting wind energy to a contained constant pressure airstream, a tower, a pivotally mounted head for said tower, a transverse shaft carried by said head, a canted oiisetting arm pivotally mounted on said transverse shaft, said rotorcompressor unit mounted on said offsetting arm with the axis of rotation of said rotor canted in a Vertical plane and passing beneath the axis of said transverse shaft whereby a component of the lift elective upon said rotor during operation tends to lift said unit. said component being resisted by the weight of said unit, and a'resilient stop limiting downward travel of said offsetting arm about said transverse head shaft.

5. In a wind rotor-compressor unit for converting wind energy to a contained constant pressure airstream, a variable capacity compressor, a tower, a pivotal mounting for said unit on said tower providing freedom for the rotor of said unit to assume a downwind position with respect to said tower, a tension loaded bar mounted in said unit and means directiy responsive to lift Variations on said rotor for moving one end of said bar, and means operatively associated with the other end of said bar for varying the capacity oi said compressor, whereby the torque requirements of said compressor are synchronized with the power output of said rotor through a wide range of wind velocity variation.

6. In a wind rotor-compressor unit for converting wind energy to a contained constant pressure airstream, a variable capacity compressor, a tower a pivotally mounted head for said 12 tower, a transverse shaft carried by said head, a canted osetting arm pivotally mounted on said transverse shaft, said rotor-compressor unit mounted on said offsetting arm with the axis of rotation of said rotor canted in a vertical plane and passing beneath the axis of said transverse shaft whereby a component of the lift effective upon said rotor during operation tends to lift said unit, means responsive to said lifting of said unit varying the capacity of said comprssor, said component being resisted by the Weight of said unit, a flexible conduit connecting said compressor with said head, an air pas` sage centrally disposed along the pivotal axis of said head a packing gland centrally disposed in said tower and communicating with said passageway, and an airline leading from said tower communicating with said packing gland.

RUSSELL R. HAYS.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 485,881 Perry Nov. 8, 1892 498,989 Perry June 6, 1893 568,794 Verne et al July 14, 1896 924,060 Hards June 8, 1909 1,000,690 Pichault Aug. 15, 1911 1,035,431 Ericson Aug. 13, 1912 1,254,737 Smithey Jan. 29, 1918 1,255,998 Fahle Feb. 12, 1918 1,299,151 Ebert Apr. 1, 1919 1,369,596 Yanacopoulos Feb. 22, 1921 2,178,047 Malme Oct. P1,` 1939 2,360,791 Putnam Oct. 17, 1944 2,369,048 Hays Feb. 6, 1945 2,460,527 Oliveros Feb. 1, 1949 FOREIGN PATENTS Number Country Date 11,864 Great Britain 1847 601,986 Germany Oct. 19, 1934 

